Cooling package system



A118. 1961 R. R. BAYUK EI'AL COOLING PACKAGE SYSTEM 3 Sheets-Sheet 1 Filed Nov. 28, 1958 SOURCE RELIEF CON T/FOL VALVE T VAL VE EXC/l.

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A118. 1961 R. R. BAYUK ETAL 2,994,515

COOLING PACKAGE SYSTEM Filed Nov. 28. 1958 3 Sheets-Sheet 2 3056723' R BQyZLk jonald 15. 5,00%

1951 R. R. BAYUK EI'AL COOLING PACKAGE SYSTEM 3 Sheets-Sheet 3 Filed Nov. 28, 1958 fnz/erzfarzs Z1 oberzf 1?. fia yuk Janelle, J5. 5

we and P 1? M16? 04 a United States Patent 9 2,994,515 COOLING PACKAGE SYSTEM Robert R. Bayuk, Cleveland, John R. Howe, Solon, and

Donald R. Spotz, Cleveland, Ohio, assignors to Borg- Warner Corporation, Chicago, 111., a corporation of Illinois Filed Nov. 28, 1958, Ser. No. 777,118 2 Claims. (Cl. 257310) This invention relates to a cooling package system, and in particular, to a cooling package system having a cooling package that is adapted to deliver coolant from a source to a heat generating device for cooling the same, the cooling package having means whereby the temperature of the coolant delivered to the heat generating device is prevented from exceeding a predetermined temperature to thereby prevent the heat generating device from exceeding a predetermined temperature.

It is well known in the art to provide various types of cooling systems for cooling heat generating devices to thereby prevent the heat generating device from exceeding a predetermined temperature. Suchcooling systems have been utilized for cooling radar power units and other electronic apparatus. These cooling systems have, of course, been utilized in many other different types of applications.

It has been found desirable to design a recirculating cooling package system having a cooling package that is made as compact as possible, portable, and is adapted to deliver coolant below a predetermined temperature for the purpose of cooling externally disposed heat generating devices.

It is therefore, an object of this invention to provide an improved cooling package system.

It is another object of this invention to provide an improved cooling package having means for drawing coolant from a source and delivering the same to an external- 1y disposed heat generating device for the purpose of cooling the device, the cooling package having means for preventing the temperature of the coolant delivered to the heat generating device from exceeding a predetermined temperature.

Another object of this invention is to provide a cooling package or unit comprising an outer hollow casing, a pump housing supported within the outer casing, the pump housing having rotatable pumping means and an inlet and an outlet respectively leading to and from the pumping means, a drive shaft rotatably supported within the outer casing and interconnected with the pumping means, a fan or rotor carried by the shaft and disposed within the outer casing, and means for rotating the shaft whereby the pumping means is adapted to draw fluid from the inlet, pressurize the same, and force the pressurized fluid out through the outlet, and whereby the rotor is adapted to cause an axial air flow through the outer casing in order to be adapted to decrease the temperature of the fluid delivered to the outlet.

A further object of this invention is to provide a cooling system comprising, a source of fluid, a pumping unit having rota-table pumping means and an inlet and an outlet respectively leading to and from the pumping means, the inlet being in fluid communication with the source whereby the pumping means is adapted to draw fluid from the inlet, pressurize the same, and force the pressureized fluid out through the outlet, valve means fluidly interconnected with the outlet and having a passage adapted to be placed in fluid communication with the outlet, a heat exchanger having an intake fluidly interconnected with the outlet intermediate the valve means and the pumping means and having a discharge adapted to be placed in fluid communication with the passage whereby at least a portion of the fluid in the outlet is adapted to be Patented Aug. 1, 1961 bypassed through the heat exchanger, a fan or rotor adapted to cause a flow of air about the heat exchanger in order to decrease the temperature of the fluid bypassed therethrough, and a temperature responsive member carried by the valve means for varying the degrees of communication of the discharge and the outlet with the pas-' sage in accordance with the temperature of the fluid in the passage to thereby tend to prevent the temperature of the fluid in the passage from exceeding a predetermined temperature.

Other and more particular objects, advantages, and

uses of this invention will become apparent from a read-.

ing of the following specification taken in connection with the accompanying drawings forming a part thereof and wherein:

FIGURE 1 is a schematic drawing illustrating a cooling package system formed in accordance with the teachings of this invention.

FIGURE 2 illustrates, in an axial cross-sectional view, a cooling package formed in accordance with the teachings of this invention and is taken on line 22 of FIG- URE 3.

FIGURE 3 illustrates, in a crosssectional view, certain operating parts of the cooling package illustrated in FIG- URE 2 and is taken on line 33 thereof.

FIGURE 4 illustrates, in a partial, cross-sectional enlarged "view, certain other operating parts of the cooling package illustrated in FIGURE 2 and is taken on line 44 thereof.

FIGURE 5 is an enlarged view of a portion of the cooling package illustrated in FIGURE 2.

Reference is now made to the accompanying drawings wherein like reference letters and numerals are used throughout the various figures thereof to designate like parts where appropriate, and particular reference is made to FIGURE 1 illustrating a cooling package system, generally indicated by the reference letter A, formed in accordance with the teachings of this invention and com prising a cooling package or unit B adapted to receive fluid or coolant from a source C through an inlet means D and discharge the same out through a passage means E to a heat generating device F for the purpose of absorbing the heat thereof to cool the same, the passage means E leading back to the source C.

The cooling package or unit B comprises an electric motor means G for driving a shaft means H interconnected with a fan or rotor I and a pumping means I, the pumping means I being adapted to draw fluid or coolant from the inlet means D, pressurize the same, and force the pressurized fluid or coolant out through an outlet means K leading to a control valve L and the fan I being adapted to cause an axial flow of air passing through the cooling package B as indicated by arrows. A heat exchanger M is carried by the cooling package B and has an intake means N fluidly interconnected with the outlet means K and a discharge means 0 fluidly interconnected with the control valve L, the heat exchanger M being so constructed and arranged that the axial air flow passes therethrough in order to decrease the temperature of the fluid bypassed through the heat exchanger M by the control valve L in a manner later to 'be described. The control valve L is adapted to be responsive to the temperature of the fluid or coolant delivered to the passage means E and is adapted to selectively direct at least a portion of the fluid in the outlet means K through the heat exchanger M in order to decrease the temperature of the bypassed fluid. In this manner, the control valve L is adapted to vary the degrees of communication of the heat exchanger discharge means 0 and the outlet means K with the passage means E to thereby vary the proportions of the coolant delivered by the heat exchanger M and the coolant delivered directly by the pumping means I permitted to pass through the passage means E in order to prevent the temperature of the fluid in the passage means E from exceeding a predetermined temperature.

A relief valve P is adapted to interconnect the outlet means K and the inlet means D whenever the pressure value of the fluid or coolant in the outlet means K exceeds a predetermined pressure value to thereby prevent the pressure value of the fluid in the outlet K from exceeding the predetermined pressure value.

The particular details of the cooling package or unit B will now be described. As shown in FIGURE 2, the cooling unit B includes an outer casing means 19 comprising a plurality of hollow outer casing sections 11 and 12 suitably fastened together in aligned relation bya plurality of bolts 13. An inner hollow casing 14 is concentrically disposed within the outer casing section 11 and is interconnected thereto by a plurality of stator vanes 15.

The inner casing 14 is substantially cup-shaped and has an opened end 16 and a closed end 17'. The closed end 17 of the inner casing 14 carries a tubular member or bearing support 18 projecting coaxially within the casing 14 and telescopically receiving a suitable bearing means 19 therein for rotatably supporting an end 20 of a drive shaft 21. Another end 22 of the drive shaft 21 is rotatably supported by suitable bearing means 23 carried by a pump housing 24 supported within the outer casing section 12 by a plurality of support members 25, 26, and 27 (see FIGURE 3). The pump housing support members 25, 26, and 27 are respectively interconnected with the outer casing section 12 at the outer ends thereof and to the pump housing 24 at the inner ends thereof.

The fan or rotor I comprises a rotor hub 28 suitably fastened to the drive shaft 21 intermediate the inner casing 14 and the pump housing 24, the rotor hub 28 overlapping the inner casing 14 at the left end of the hub 28. The rotor hub 23 carries a plurality of rotor blades 29 which, when rotated, are adapted to cooperate with the outer casing means 10 and cause an axial flow of air through the outer casing means 10. It should be noted that the exterior surfaces of the inner casing 14, rotor hub 28, and pumphousing 24 define a substantially bullet shaped unit within the outer casing means 10 to thereby provide a tapering annular air flow passage within the outer casing means 10.

. The pump housing 24 is provided with a cavity 30 at one end 31 thereof and a pair of parallel, intersecting bores 32 and 33 at another end 34 thereof. A pair of intermeshing gears 35 and 36 are disposed respectively in the bores 32 and 33 and form the pumping means I illustrated in FIGURE 1. The gears 35 and 36 are respectively provided with centrally projecting journals 37 and 38 which are rotatably supported within the pump housing 24. The journal 37 of the gear 35 is provided with a vertically disposed tongue member 39 which is adapted to be received in an accommodating vertically disposed slot 40 formed in one end of a drive link 41. The drive link 41 has a horizontally disposed slot 42 formed in the other end thereof which is adapted to receive a horizontally disposed tongue member 43 formed on the end 22 of the drive shaft 21. In this manner, any misalignment between the journal 37 of the gear 35 and the drive shaft 21 is compensated for by the drive link 41. Suitable sealing means 44 are disposed within the cavity 30 to prevent fluid leakage past the end 31 thereof. The cavity 30 is fluidly interconnected to a drain plug 45 carried bythe outer casing section 12 by a passage 46 formed in the'pump housing support member 25. In this manner, any fluid which has escaped from the pumping means I into the cavity 30 can be drained to the exterior of the cooling package or unit B'through the passage 46.

-As shown in FIGURE 3, a coupling member 47 is in- "t'erconnected to the outer casing section 12 adjacent the support member 26. The inlet means D of the cooling package passes through'the'coupling member'47 and'the pump housing support member 26 to the inlet side of the rotatable pumping means 35, 36. A pulsating dampening means Q is disposed within the coupling member 47 and comprises a bellows assembly 48 which is adapted to be responsive to the flow of the fluid or coolant conveyed from the source C through the inlet means D. Upon a sudden surge of the flow of fluid or coolant entering the coupling member 47 through the inlet means D. the force thereof acting against the bellows 48 tends to contract the same to thereby increase the effective vol ume of the inlet means D in the coupling member 47. By increasing the effective volume of the inlet means D in the coupling member 47, the flow of fluid passing therethrough is retarded thereby providing an even flow of fluid to the pumping means J. Similarly, upon a sudden decrease in the flow of fluid from the source C through the inlet means D, the bellows 48 will expand to thereby decrease the effective volume of the inlet means D in the coupling member 47 to speed up the flow of fluid therethrough and rus maintain a steady flow of fluid from the source C through the inlet means D to the rotatable pumping means J.

The outlet means K of the cooling package B leads from the outlet side of the gears 35 and 36 and passes through the pump housing support member 27 and the outer casing section 12 to the control valve L. In this manner, upon rotation of the drive shaft 21, the gears 35 and 36 are adapted to draw coolant from the inlet means D, pressurize the same, and force the pressurized coolant out through the outlet means 27 to the control valve L.

A plate 49 is suitably fastened to the right end 34 of the pump housing 24 by a plurality of bolts 50, the plate 49 cooperating with the pump housing 24 to provide pumping cavities for the rotatable gears 35 and 36. The relief valve assembly P is attached to or formed integrally with the plate 49 and comprises a housing 51 having a passage 52 interconnected with the outlet means K at 53 and interconnected with the inlet means D at 54. A spring biased relief valve 55 is disposed in the passage means 52 and is adapted to engage a valve seat 56 to prevent fluid communication between the outlet means K and the inlet means D through the passage 52. When the force of the pressurized fluid within the outlet means K exceeds a predetermined value, as determined by the particular compression force setting of a spring 57 acting against the relief valve 55 tending to maintain the same against the valve seat 56, the relief valve 55 is unseated and permits fluid communication between the outlet means K and the inlet means D. In this manner, the relief valve assembly P prevents the pressure value of the pressurized coolant delivered through the outlet means K from exceeding a predetermined pressure value.

An armature 58 is disposed within the inner casing 14 and is suitably secured to the drive shaft 21. A stator 59 is secured to the casing 14 and is disposed concentrically about the armature 58, the armature 58 and stator 59 comprising the motor means G illustrated in FIGURE 1. Electrical current is supplied to the motor means G from a source (not shown) through suitable switching means 60 secured to the outer casing means 10 of the cooling package B. In this manner, the motor means G can be selectively operated to cause rotation of the drive shaft 21 and thus rotation of the rotor 'I and the gears 35, 36 of the pumping means I.

The double pass, substantially rectangularly shaped heat exchanger or radiator M is disposed at the right end of the outer casing means '10 and is suitably fastened thereto in any feasible manner. The intake means N of the radiator or heat exchanger M is placed in fluid communication with the outlet means K by a passage 61 formed in the outer casing section 12. As shown in FIGURE 3, the discharge means 0 of the heat exchanger M is fluidly interconnected with the control valve L by a-passag'e 62'formedin-the outercasing section 12.

The control valve L comprises a housing 63 suitably secured to the outer casing section 12. A bore 64 is formed in the valve housing 63 and defines an internal peripheral surface 65 within the valve housing 63. A plurality of axially spaced annular grooves 66, 67, 68, and 69 are formed in the internal peripheral surface 65 of the valve housing 63. The annular grooves 66 and 69 are respectively sealed from the exterior of the valve housing 63 by end plates 70 and 71. A cylindrical, axially movable valve member 72 having an external peripheral surface 73 is disposed within the bore 64 of the valve housing 63. The peripheral surface 73 of the valve member 72 cooperates with the peripheral surfaces 65 of land portions 74, 75, and 76 of the valve housing 63 to prevent fluid communication between the annular grooves 6669 through the bore 64 the land portions 74, 75, and 76 being defined by the annular grooves 6669.

The valve member 72 is provided with a longitudinal bore 77 interrupting one end 78 thereof and interconnecting with the annular groove 69 through a plurality of ports 79 formed in another end 80 of the valve member 72. The end 80 of the valve member 72 is fastened to the end plate 71 by a temperature responsive bellows 81 disposed within the annular grooves 69 of the housing 63 and interposed between the valve member 72 and the end plate 71. The valve member 72 is provided with an annular groove 82 having a width slightly greater than the width of the land portion 75 of the valve housing 63. The annular groove 82 is interconnected with the bore 77 formed in the valve member 72 by a plurality of apertures 83.

The annular groove 68 formed in the valve housing 63 is interconnected with the outlet means K by a passage 84 formed in the valve housing 63 and the annular groove 67 is interconnected with the discharge means of the heat exchanger M by a passage 85 formed in the valve housing 63. The annular groove 69 is interconnected with the passage means E, illustrated in FIG- URE 1, by a suitable coupling means 86.

The temperature responsive bellows 81 is responsive to the temperature of the fluid delivered to the passage means B through the valve member 72. In this manner, the bellows 81 determines the axial position of the valve member 72 relative to the valve housing 63. When the valve member 72 is in the position illustrated in FIGURE 3, equal degrees of fluid communication is permitted between the annular grooves 68 and 67 and the bore 77 formed in the valve member 72 as the annular groove 82 in the valve member 72 straddles the land portion 75 of the valve housing 63 whereby equal amounts of fluid from the heat exchanger M and directly from the pumping means I is permitted to pass through the bore 77 to the annular groove 69 and thus to the passage means E.

If the temperature of the fluid delivered to the passage means E falls below a predetermined temperature, the bellows 81 will contract thereby causing axial movement of the valve member 72 to the left to decrease the degree of communication between the annular groove 67 and the annular groove 69 and to correspondingly increase the degree of communication between the annular groove 68 and the annular groove 69. amount of the coolant which is delivered to the passage means E comes directly through the outlet means K from the pumping means I than the amount of fluid bypassed through the heat exchanger M in order to tend to raise the temperature of the fluid in the passage means E to the predetermined temperature.

If the temperature of the fluid delivered to the passage means E increases above the predetermined temperature, the bellows 81 will expand thereby causing axial movement of the valve member 72 to the right. Upon axial movement of the valve member 72 to the right, the degree of fluid communication between the annular groove 68 and the bore 77 of the valve members 72 de- In this manner, a greater' creases and the degree of fluid communication between the annular groove 67 and the bore 77 increases. In this manner, a greater portion of the fluid delivered to the passage means E comes from the heat exchanger M than directly from the pumping means I in order to tend to lower the temperature of the fluid in the passage means E to the predetermined temperature.

It can be seen that when the degree of communication between the annular grooves 68 and 69 is decreased, a greater amount of fluid delivered to the outlet means K is bypassed through the heat exchanger M than the amount bypassed when the degree of communication is increased. In this manner the total amount of fluid delivered by the pumping means I passes to the passage means E through the control valve L even though the control valve L varies the amount of fluid by passed through the heat exchanger M. Therefore the movement of the valve member 72 to the right or left does not have any effect on the pressure value of the coolant delivered by the pumping means J.

The operation of the cooling package system A will now be described. Upon operation of the motor means G by the switching means 60, the drive shaft 21 will be rotated causing rotation of the fan or roto I and the gears 35 and 36 of the pumping means I. The rotating gears 35 and 36 will draw coolant from the source C through the inlet means D, pressurize the same, and deliver the pressurized coolant out through the outlet means K. Assuming that the control valve L is in the position illustrated in FIGURE 3, half of the amount of coolant passing through the outlet means K to the control valve L is bypassed to the heat exchanger M through the intake means N thereof. The remaining amount of the coolant in the outlet means K enters the annular groove 68 and passes to the annular groove 69 through the bore 77 formed in the valve member 72. Similarly, the portion of the coolant bypassed through the heat exchanger M passes out through the discharge means 0 into the annular groove 67 and passes through the bore 77 of the valve member 72 into the annular groove 69. The coolant delivered to the annular groove 69 is directed thorugh the passage means E to the heat generating device P where the coolant absorbs the heat generated by the device F to thereby decrease the temperature of the device F. After the coolant has absorbed the heat from the heat generating device F, the coolant is returned to the source C by the passage means E.

Is should be understood that the air flow created by the fan or rotor I and being utilized to cool the coolant bypassed through the heat exchanger M can also be utilized to cool by convection currents other devices, disposed in the axial air flow and adjacent the cooling package B.

If the temperature of the coolant within the passage means E increases above a predetermined temperature, the bellows 81, sensing the increase in temperature, will cause movement of the valve member 72 to the right thereby causing a greater amount of the fluid to be bypassed through the heat exchanger M than normally thereby permitting a greater portion of the fluid supplied to the passage means E to be taken from the discharge means 0 of the heat exchanger M than the portion of the coolant taken directly from the pumping means J. Since the axial air flow caused by the fan I is passing through the heat exchanger M, the fluid bypassed therethrough has the temperature thereof decreased as the air absorbs the heat of the fluid bypassing through the heat exchanger M. It can be seen that the temperature responsive bellows 81 can completely close off the communication between the annular groove 68 and the annular groove 69 thereby causing the entire flow of coolant through the outlet means K to be bypassed through the heat exchanger M and thus to the passage means E.

Similarly, if the temperature of the fluid within the P age means E decreases below a predetermined pres sure value, the bellows 81 contracts thereby causing movement of the valve member 72 to the left decreasing the degree of communication between the annular groove 67 and the annular groove 69 and increasing the degree of communication between the annular groove 68 and the annular groove 69 whereby a greater amount of the coolant delivered to the passage means E comes directly from the pumping means I than the amount of coolant bypassed through the heat exchanger M to thereby tend to increase the temperature of the coolant in the passage means E to the predetermined temperature. It can be seen that the valve member 72 can completely close olf communication between the heat exchanger M and the passage means E whereby the entire amount of fluid directed to the passage means E comes directly from the pumping means 1.

Therefore, it can be seen that there has been described an improved cooling package or unit which can be utilized in many cooling applications by merely interconnecting the inlet means to a source of coolant and the outlet means to a passage means leading to the device or devices to be cooled thereby, the cooling package containing all the necessary operating parts to tend to maintain the temperature of the fluid delivered thereby at a predetermined temperature value.

While this invention has been disclosed in connection with a certain specific embodiment thereof, it is to be understood that this was by way of example rather than limitation, and it is intended that the invention be defined by the appended claims.

What is claimed is:

1. In a cooling system for cooling a device subject to being heated and comprising: a source of fluid; a pumping unit having rotatable pumping means disposed in a pump casing and having an inlet and an outlet respectively leading to and from said pumping means, said inlet being in fluid communication with said source Whereby said pumping means draws fluid from said inlet, pressurizes the same, and forces the pressurized fluid out through said outlet; means defining a passage adapted to be placed in fluid communication with said outlet, said passage leading to said device and from said device back to said source; a heat exchanger having an intake fluidly interconnected with said outlet and having a discharge adapted to be placed in fluid communication with said passage whereby at least a portion of the fluid in said outlet is adapted to be bypassed through said heat exchanger; a fan adapted to cause a flow of air about said heat exchanger in order to decrease the temperature of said fluid bypassed th rethrough: a motor for driving said fan and said pumping means and means for varying the degrees of communication of said discharge and said outlet with said passage to thereby regulate the temperature of the fluid in said passage, the improvement comprising a hollow casing open at both ends; said motor, fan and pump casing being disposed substantially within said hollow casing, a plurality of members connected to said pump casing and to said hollow casing and supporting said pump casing in said hollow casing, means defining passageways in said members and in communication with said pump, one of said passageways comprising said pump inlet and the other of said passageways comprising said pump outlet, and said heat exchanger being connected to one of the open ends of said casing.

2. In a cooling system for cooling a device subject to being heated and comprising: a source of fluid; a pumping unit having rotatable pumping means disposed in a pump casing and having an inlet and an outlet respectively leading to and from said pumping means, said inlet being in fluid communication with said source whereby said pumping means draws fluid from said inlet, pressurizes the same, and forces the pressurized fluid out through said outlet; valve means interconnected with said outlet and having a passage adapted to be placed in fluid communication with said outlet; means for conveying fluid from said passage to said device and from said device back to said source; a heating exchanger having an intake fluidly interconnected with said outlet intermediate said valve means and said pumping means and having a discharge adapted to be placed in fluid communication with said passage whereby at least a portion of the fluid in said outlet is adapted to be bypassed through said heat exchanger; a fan adapted to cause a flow of air about said heat exchanger in order to decrease the temperature of said fluid bypassed therethrough; a motor for driving said fan and said pumping means and a temperature responsive member carried by said valve means for varying the degrees of communication of said discharge and said outlet with said passage in accordance with the temperature of the fluid in said passage to thereby tend to prevent the temperature of the fluid in said passage from exceeding a predetermined temperature, the improvement comprising a hollow casing open at both ends; said motor, fan and pump casing being disposed substantially within said hollow casing, a plurality of members connected to said pump casing and to said hollow casing and supporting said pump casing in said hollow casing, means defining passageways in said members and in communication with said pump, one of said passageways comprising said pump inlet and the other of said passageways comprising said pump outlet, said heat exchanger being connected to one of the open ends of said casing, said hollow casing having an enlarged section, means defining first and second passageways in said enlarged section, said first passageway communicating said outlet passageway with said temperature responsive member and said second passageway communicating said temperature responsive member with said heat exchanger.

References Cited in the file of this patent UNITED STATES PATENTS 2,064,244 Davies et al. Dec. 15, 1936 2,307,341 Van Vulpen et al. Jan. 5, 1943 2,308,408 Wall Jan. 12, 1943 2,680,007 Arbuckle June 1, 1954 2,829,869 Philipp Apr. 8, 1958 2,839,274 Polin July 17, 1958 

